Forming machine



A. FIBISH FORMING MACHINE Oct. 1,' 1963 Filed Sept. 17, 1959 Oct. 1,1963 A. FIBISH 3,105,270

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United States Patent 3,105,270 FGRMENG MACHINE Arthur Fibish, ProspectHeights, 11L, assignor to illinois Tool Works Inc, a corporation ofDelaware Filed Sept. 17, B59, Ser. No. 840,611 11 Claims. (Cl. 18-49)This invention relates generally to an apparatus for forming articles ofmanufacture out of sheet plastic materials, and more particularlyrelates to a machine for forming plastic containers of the thin wallvariety.

In the art of forming containers and the like from plastic materials ofthe thermoplastic variety, two major methods have been used heretofore,namely, that of injection molding and the second type which may bedenominated as pressure molding. In the latter method, a pressuredifferential is created across a web or membrane of thermoplasticmaterial to cause it to move into engagement with the mold member. Theapparatus to be discussed hereinafter in greater detail generallyrelates to the second type of molding process and the preferredapparatus employs the combination using a pressure differential alongwith a mechanical drawing of the sheet material to obtain the desiredresults.

While containers may be formed by a blow molding or vacuum moldingprocess without any mechanical engagement of the web of heatedthermoplastic material to form the container, it has been found thatmore uniform results are obtained by mechanically drawing the heatedthermoplastic material with a mandrel to cause a major deformation ofthe web or sheet stock. The web or sheet stock is first engaged by aclamp means, the mandrel then engages and draws the thermoplasticmaterial, the thermoplastic material is then blow-n or drawn intocontact with a surrounding chilled mold cavity by a fluid pressuredifferential (preferably air pressure differential) which causes theseparation of the thermoplastic material from the mandrel and engagementwith the cooled mold cavity. The next step in the operation is to severthe drawn and formed thermoplastic product from the remaining web orsheet stock and finally to eject the finished item from the mold.

Prior art types of machines of types known to me which are adapted topractice the aforedescribed general method of manufacture have hadcertain major deficiencies. For example, one problem of the prior artmachines was that the wen of the major cam bearings and of the cams perse in the machine was excessive. Another problem encountered was thatthe machine would have a tendency for certain expensive machined partsto break unless extreme care was exercised, such breakage occurring uponinitial warmup of the machine before it was in condition for continuousproduction. The prior art machines also had a high amount of vibrationalpounding on each cycle of the machine due to the construction thereof.

A further prior art problem frequently encountered was the inaccuracy ofthe feeding mechanism of the machines which caused a much higher amountof scrap than was necessary, said extra scrap including a high number ofmalformed products, such as containers. These malformed containers wereoften produced by engagement of the mold with a portion of the web orsheet material which had been previously acted on by the mold. Further,the misalignment of the web of material in the horizontal plane wouldcause jam ups and other problems.

A still further problem encontered in prior art devices was that uponoccurence of a jam up or pile up of the web of material in the machine,the mechanism for heating the thermoplastic material to the requiredtemperature for molding would either cause the plastic material newPatented Get. 1, i963 'ice to catch fire, or in the alternative causethe plastic to be heated to a point Where it would at least melt and rundown onto other parts of the machinery necessitating a complete shutdownwhile the mess was cleaned up.

In order to produce products, such as containers, of the typecontemplated herein competitively out of plastic materials, it isnecessary that a high operational rate of speed of the machinery beefiectuated. The prior art machines have certain inherent deficienciessuch as poor mass in motion relationship, poor feeding mechanisms, etc.,which make it impossible for the speed to be changed by any significantfactor so as economically to increase production from a single machine.Also the known prior art machinery was not well adapted to adust tovarying thicknesses in material or varying sizes of material. This posedmajor problems in feeding and molding operations whenever a slightchange was encountered in the sheet stock.

It is a general object of this invention to provide an apparatus whichovercomes the aforenoted problems.

It is another object of this invention to provide an apparatus which hasa construction affording an operation which cushions the cycling opposedmovement of the mandrel and mold means to provide a somewhat resilientaction which results in less vibration of the machine, operation at amuch lower noise level, and a considerably longer machine life; allwithout sacrifice of desired functions.

More particularly, it is an object of this invention to provideapparatus for the manufacture of thin wall products of plastic materialwhich has a construction which will accommodate jam ups or pile ups ofcontainers in the mold cavity area without causing breakage of theapparatus and without necessitating a complete shutdown of theapparatus.

It is a 'further object of this invention to provide a machine whereinthe mandrel or male mold member is separately and positively driven by adrive shaft separate from the shaft driving the female mold memberthereby affording a machine which may be operated at a considerablyfaster speed.

It is further an object of this invention to provide an apparatus of theaforedescribed general characteristics which includes a driven movableclamp member which is actuated separately and apart from the male andfemale mold means which in turn permits increase in the operatipnalspeed of the apparatus, as will be shown hereina ter.

It is a further object of this invention to provide apparatus of theaforenoted general type which includes feed mechanism for accuratefeeding (including stopping and starting) of the web material of varyingthicknesses and widths.

It is a further object of this invention to provide apparatus of theabovedescribed nature which includes a safety feature constructioneffecting quick removal of the heater apparatus from association withthe web of material whereby the aforementioned fires and gum-ups of themachine are eliminated during unforeseen stoppages of the machine.

It is a further object of this invention to provide a production machinewhich has a high volume production capacity and which may be quicklyconverted to the manufactoring requirements for varying types ofproducts of varying contours and dimensions, the conventability of themachine greatly enhancing the economic usefulness thereof.

It is therefore generally an object of this invention to provide anapparatus of the aforementioned type which has lower maintenance cost,is trouble-free in operation, has an exceedingly high volume productioncapacity, has a positive but cushioned action, and includes other fea- 3tures as will be set forth which adapt it for the purpose for which itwas designed.

The novel features that are characteristic of the inven tion are setforth with particularity in the claims. The invention itself, however,both as to its organization and its mode :of operation, together withadditional objects and advantages thereof, will best be understood bythe following description of a specific embodiment when read inconnection with accompanying drawings in which:

FIG. 1 is a side elevational view of an apparatus embodying myinvention.

FIG. la is a semi-diagrammatic view of one article of manufacture thatmay be produced by the apparatus shown in FIG. 1;

FIG. 2 is a sectional view along line 2-2 of FIG. 1;

:FIG. 3 is a sectional view along line 33 of FIG. 1;

FIG. 4 is a semi-diagrammatic view of a portion of the electricalcircuitry for the feed apparatus for the machine shown in FIGS. l-3inclusive.

FIG. 5 is a semi-diagrammatic sectional view of the apparatus takenalong line 5-5 of FIG. 1, said view having certain dimensionalrelationships greatly exaggerated for purposes of illustrative clarity;

FIG. 5a is an isometric fragmentary perspective view of the adjustmentmeans used in the machine illustrated;

[FIG 6 is an elevational view along line 66 in FIG. 1;

FIG. 7 is a fragmentary view along line 77 in FIG. 6;

FIG. 7a is a fragmentary perspective View of a portion of the deviceshown in FIG. 7; 7

FIG. 8 is an isometric perspective view of another portion of theapparatus illustrated in FIG. 7;

FIG. 9 is a view taken along line 99 of FIG. 1;

FIG. 9a is a View similar to FIG. 9 with certain components removed;

FIG. 9b is a cross-sectional view along lines 9b-9b of FIG. 9a;

FIG. 10 is a view along line 1010 of FIG. 9;

FIG. 11 is a view along line 1111 of FIG. 10;

FIG. 12 is an enlarged view along line 1212 of FIG. 13;

FIG. 13 is a view taken along line 13-13 of FIG. 12;

FIG. 14 is an enlarged fragmentary detailed elevational view of aportion of the feed mechanism taken along line 1414 of FIGURE 15;

:FIG. 15 is a view along line 15-45 of FIG. 14;

FIG. 16 is a fragmentary isometric perspective view of the parts shownin FIGS. 14 and 15;

FIGS. 17-20 are semi-diagrammatic views of the rotational movements ofthe cams and the sequential relative movement of the parts of theapparatus shown in the foregoing figures;

FIG. 21 is an enlarged fragmentary sectional view of a portion of theapparatus shown in FIG.

FIGS. 22-24 are semi-diagrammatic views similar to FIGS.17-2O showingthe next succeeding positions of the various components during thecycling of the device; and I FIG. 25 .is an enlarged fragmentary View ofa portion of FIG. 23'.

Returning now 'to FIG. 1 of the drawings, the invention relates to amachine 39 which is designed to manufacture thin wall products fromsheet stock of plastic material 33, one such product being a thin wallcup or container 32, as shown semi-diagrammatically in FIG. la of thedrawings. While this specification will discuss the machine in terms ofmanufacture of the cups as shown, the term should not be consideredlimiting as the invention has wide application to the manufacture ofplastic articles of many sizes, shapes, natures and uses.

Before describing the apparatus in detail, it Will perhaps be helpful todiscuss the major components of the machine and the manner in which itfunctions. The machine 30 is designed to receive a web of suitablethermoplastic material 33, for example polystyrene, from a suitablesupply roll 34, said web 33 being fed into the machine 36 by suitablefeed means 36. The feed means accurately and intermittently supplies theweb 33 to the ma chine past temperature controlling means 38 whichassures that the web of the material is at the correct temperature forthe subsequent molding operations within the machine 30.

As perhaps best shown in semi-diagrammatic views such as FIGS. 5 and17-25, the feed means delivers the material for engagement by the clampmeans 40 which firmly fixes same in a precise location so that the malemandrel means '42 may mechanically draw the material to a predeterminedposition whereupon an air pressure differential is impressed across theweb causing the material to be brought into engagement with the moldmeans 44 to form the desired shape of the container. The for-med item isthen severed from the web and ejected from the machine by suitablemeans, the web material that is remaining continuing on through themachine to a scrap salvaging operation for regeneration into sheetmaterial for re-circulation through the machine.

As is perhaps best shown in the semi-diagrammatic view of FIG. 5, themandrel means 42 are actuated by an actuating means 46 and the moldmeans 44 are actuated by a different and completely separate actuatingmeans 48, both the mold and mandrel means being movable in a prescribedsequential relation to accomplish the foregoing. Now to a more detaileddescription of the machine 30 and its operation.

A motor 52 (shown in FIG. 5) is connected to a source of power (notshown) and supplies the rotative movement for the heavy pants of themachine. The motor 52 is provided with an output shaft 54 leading to amiter gear unit 56 which has a first output shaft 58 and a second outputshaft 60 which are in a one to one ratio with input shaft 54. Shafts 58and 60 are respectively connected to lower and upper worm gear units 62and 64, respectively having right-angle output shafts 65 and 67 whichmay be rotated on the order of 30 to 1 step down ratio relative toinput. The first or lower output shaft 66 is adapted to drive the loweractuating means 48 and has a force transmitting connection or drivingmember 68 mounted on the end thereof and having axially projecting lugs70 on its face. The upper output shaft 67 is similarly formed with anend mounted driving connection member 74 having similar axiallyprojecting lugs 76 on the face thereof.

The lower shaft '66 together with the force transmitting connectingmember 68 is adapted to drive a lower cam shaft 78 through a matingdriven member 86 having slots 81 therein which are co-actable with anddriven by the axial lugs 70 on member 63. It Will be noted that the lugs70 of member 68 project into the slots 81 in the member 8% so as toprovide a positive rotational driving connection while affording anaccommodation to axial movement of the shaft 78 (or relative wobbling ofthe members 68 and without adversely affecting the connection. The lowercam shaft 78 is rotatably mounted in spaced spheroidal self-aligningbearing means 82 which are suitably mounted near the opposite ends ofthe shaft on a base 84.

The upper cam shaft 86 is in the same manner described re member 78rotatably mounted in bearing means for movement when driven by the upperoutput shaft 67 through the force transmitting driving connection 74which engages a driven member 83 having similar slots 89 receiving lugs76 and afi'ixed to the end of the shaft 86. It will be noted that theupper bearing means 90 are mounted on a crown 92 spaced from the basemember by a plurality of suitable upright spacer members 94 as shown inFIG. 1 and FIG. 6 of the drawings.

As will be noted from FIG. 5 of the drawings, the,

driving and driven connection means and the bearing means of therespective lower and upper cam shafts 78 and 86 are of a configurationwhich assures that they will easily accommodate a rather largedeflection of the center of the cam shafts. This deflection feature notonly cushions the vibrations but permits substantial jamups of materialin the molding parts of the machine (as shall later be explained)without impairing either the driving connection between members '74- and83 and me. bers 63 and 80 without seriously affecting the amount of wearon the bearings 82 and as. Further, breakage of expensive parts issubstantially reduced. These features have been found in practice to besignificantly important. While in FIG. 5, the shafts 7S and as have beenshown with an exceedingly large deflection, this has been exaggeratedsolely for purposes of illustration rather than to show the actualamount of deflection occurring.

Cam shaft '7 8 (the lower cam shaft as viewed in FiGS. 1, and 6 of thedrawings) is operable to drive the mold means 44 and the lower clampmeans each being independently driven by a separate cam means. Acentrally located cam means 98 is mounted on lower cam shaft and isoperable to drive the movasle lower clamp means 96 of the machine whichis located near the middle thereof. The lower clamp means 96 comprises aclamping plate 99 that directly engages the underside of the material 33and is formed with a plurality of aperture Iii-i) each having a raisedmargin 1 31. The clamp plate 99 is moved up and down to cause the raisedmargins ltll to come into and out of engagement of the material 33. Suchmovement is effected by four spaced push rods 102 which are mounted toplate as at one end and are mounted to a carriage or yoke 164 at theother end by suitable nuts threaded onto the ends thereof as shown inFIG. 3. The carriage or yoke l d-4 s rounds the cam means 98 andcomprises a pair of spaced horseshoe-shaped plates 1% and 1% which arefixedly mounted together at the bottom of the yoke by a suitable spacermember 11% which connects the bottom legs of the plates. Intermediatethe ends of plates res and are horizontally outwardly extending pairs ofstruts M2 and 116 which are connected together at their extremities by apair of spacer members 114 as shown. Each of the horizontally extendingstruts 112 and lid is formed with transversely extending lugs 118 whichare adapted to engage and mount the four push rods 162, said rods alsoextending through spaced supports 23.9 which are mounted above the lugs118 on plates 1% and The carriage or yoke 1% is moved upwardly anddownwardly in accordance with the rotational movement of shaft 73 by acam follower roller 122 which is rotatably mounted on a shaft 126 andwhich is located near the top of and journalled to the twohorseshoe-shaped plates 1% and M23. The cam roller 1'22 follows theouter surface 125 of cam means 98, as well understood in the art. Thegeneral shape of the cam surface 126 is perhaps best shownsemi-diagrammatically in FIGS. 17-24 for purposes to be explainedhereinafter. The carriage or yoke 1'34- is guided in its upward anddownward movement by suitable rollers 128 which are located at each ofthe four corners of the carriage for coaction with the edges of the legsof plates iii-5 and As shown in FIG. 7, the rollers 128 are rotatablymounted in fixed position to horizontally extending members 113% whichin turn are fixed to lugs 127 of cross members 129 which extend betweenand are fixed to frame uprights 94.

The mold means 44 is also actuated by the lower cam shaft 78 andcomprises a plurality of individual frusto conical depressions or moldcavities 131 (PIGS. 17-19) formed in mold members 132 (see also FIG. 6)which may be suitably mounted on a large platen or bolster 134. A hollowcradle 136 having depending legs 138 and Mil is shown in perspective inFIG. 7a. As shown in FIG. 7, the cradle 136 depends from and is mountedto platen 134 through spacers 152 (FiGS. 5 and 6, as will be discussedlater) by elongated spaced bolts l37. Rotatably mounted near the bottomof each of the two cradle legs 138, 144i is a pair of cam rollers 141,142. The rollers 141 and 142 coact with spaced identical cams 143, 144(FIGS. 5-7, 17-20 and 224.4) mounted on shaft 78 for rotation therewith.The cams 143, 144 have cam flanges 145, 14%6 associated therewith toassure positive engagement of the rollers 141, 1 .42 with the cams 143,144 during the opening sequences of the operation to pull down the moldas will become apparent. It will also be apparent that the surfaceconfiguration of the cams 143, 144 is substantially as shown in FIGS.17-24 to afford a sequential operation as shall be later explained.

A plurality of upright cylindrical guide posts 148 preferably four innumber, is located Within the confines of the machine as defined by thefour upright members 94 and serve as precision guide rods for themovement of the mold means 44 and also for the mandrel means 42 which isspaced thereabove. Suitable ball bearing guide sliding members 59 areassociated with the corners of the mold means bolster 134 and with theguide rods 148 to assure easy sliding movement thereof in a verticalplane in timed relation to the rotational movement of the cams 143, 144.

it is important that there be an adjustment means between the cradle136- and the platen 134, and to this end suitable adjustable spacermembers 152 (see FIG. 5a) are inserted in the space therebetween insurrounding relation to the four bolts 137. Proper location of thisadjustment means 152 assures a quick, easy change-over of the machine toaccommodate it to varying thickness of materials as well as toaccommodate different mold configurations. I have found that one veryacceptable expedient for adjustment means is a split ring mechanismwhich is held in place by an annular spring (not shown) mountable in thecentral annular groove 153 formed in the outer side walls of the splitring. The split ring mechanism when used with shims assures accurateadjustment of the height of the platen 134 to the cradle 136 for thedesired tolerance.

Referring now to FIGS. 6 and 7, a fixed plate 154 is shown mountedwithin the hollow lower cradle res and is fixed to a pair of spacedshort channels 155, said plate 154 being generally horizontally alignedfor coaction with the ends of mold knock out plugs 156. The channels 155in turn are mounted on cross members 157 which in turn are mounted tothe frame. (It should be noted that channels 155 are not shown in FIG. 7for purposes of clarity.) The plate 154 is formed with suitableapertures therein for the push rods 16 2 so that the latter may moverelative to the fixed plate 154. It is apparent that the arms 133, 14%of the cradle mechanism surround the plate and are relatively movablethereto so that the mold means 44 moves relative to the plate 154 thusunder certain conditions to cause movement of the mold relative to themold plugs 156 which bottom on said plate. The plugs 156 per so are eachformed with an enlarged head which forms the bottom of the mold cavity131. As will be explained, the head of the knock out plug ejects orknocks out the finished molded item from the confines of the mold cavity131.

The individual molds 132 each have a lip portion 16 (see especiallyFIGS. 2-1 and 25) which is annular in configuration and extendsupwardly, the outer edge of portion rec being formed with a pair ofaxially (vertically) spaced shoulders 162 and 164. These shoulders 162and 164 serve clampingly to engage and also to sever the web material 33when coacting with the mandrel means 42 (lining the forming operation aswill become apparent from the descriptions following hereinafter. Thisstructure and the operation thereof form the basis of the copendingapplication of Bryant Edwards having Serial No. 763,668 and assigned tothe assignee of the instant invention.

The mandrel means 42 is spaced above the sheet 33 and essentiallycomprises a plurality of plugs or mandrels 166 which are telescopicallymovable within the mold cavity 131. The individual plugs or mandrels 166are mounted on a ram or upper platen 168 which, through four bolts 169(FIGS. and 6) is spacedly mounted to an upper cradle 170 having spacedcradle arms, 171, 172 similar to the arms of cradle 136 used in thelower portion of the machine. A pair of rollers 173, 174 is mounted onthe upper ends of the cradle arms 171, 172 for coaction with a pair ofspaced cam track members 175, 176 fixedly mounted to the upper cam shaft86. It will be observed that cam shaft 86 rotates in a directionopposite to the direction of rotation of cam shaft 73. The upper platenor ram 168 is mounted at its corners for sliding up and down movement onsuitable slide members 178 which are similar to and spaced above slidemembers 150. The slides 178 also ride on upright guide rods 14%. Fourspaced adjustment means 180, similar to adjustment means 1'52 describedhereinbefore, are provided for the upper portion of the mechanismintermediate the platen 168 and cradle 170 to accomplish adjustment tovariable positions of the mandrel members to afford a quick, yet easyand accurate method of adjustment for variable thicknesses of materialsand/ or for manufacturing items of diiferent overall height.

a The upper clamp means 182 is relatively fixed and is cooperable withthe lower clamp means 95 and comprises a plate 181 having apertures 183with downwardly projecting margins "185 opopsitely positioned to margins1 on plate 99. The plate 181 is fixedly mounted to the crown 92 by meansof a plurality of rods 134, the latter having a very short lost motionspring loading arrangement 186 whereby the clamp means 182 is biased ina downwardly direction and may have a quarter-inch or so lost motionmovement in an upwardly direction upon clamping engagement with thematerial 33 together with the lower clamp means '26. It will be realizedthat the apertures 183 in the upper clamp means 182 are respectivelyaligned with the apertures 106 in the lower clamp means and that each ofthe apertures 1%, 183 is slightly larger than the mold and mandrel meansas shown in FIGS. 17-25.

Surrounding the individual mandrels 166 at the upper ends thereof areslightly larger annular members 188 (FIGS. 17-25) each having a centraldepression 189 which defines a leading clamping and cutoff edge 19%which is adapted to trap the web of material between the upper lipportion 169 and shoulders 162 and 164 of the mold means as shown inenlarged views of FIGS. 21 and 25. Also, the mandrels 166 have airpressure means associated therewith (not shown) so as to admit air underpressure to one side of the material during a portion of the formingcycle. The structure and function of the parts referred to are also apart of said copending application in the name of Bryant Edwardspreviously referred to. The sequence of the operation of the variouscomponents described hereinbefore will be set forth in moreparticularity after dmcnibing the apparatus for feeding the materialthrough the device.

The feed mechanism 36 for the material is separately actuated, thoughcoordinated in timed relation, with the movements of the mold andmandrel means 44, 42. As noted heretofore, the material or web 33 may bestored at the front end of the machine on a suitable storage roll 34which is mounted to the ends of a pair of crossframe members 192. Framemembers 192 are fixed to horizontally spaced upright frame members 193and 194. It is sometimes desirable and possible, to run the material 33directly into the feed mechanism from the output end of an extrudermechanism (not shown). Speaking broadly, as the material leaves theextruder, or in the alternative the storage roll 34, it first proceedsthrough alignment means 1%, thus through measuring and control means 193for engagement by a moving clamp means 199 which physically moves thematerial through the apparatus. The alignment means 1% assures thematerial 33 being fed into the machine in accurate alignment forsubsequent engagement by the moving clamp mechanism 19?, and alsoassures accurate measurement by the measuring and control means 198.

The alignment means 196 comprises a type of apparatus roughly pantographin nature which is shown in FIGS. 9- 11. As shown, the alignment means196 comprises a pair of short spaced apart web engaging members 200 and2&2 aligned transversely of the web and having rounded leading andtrailing edges 264, 206 and 208, 21G respectively which are located onand'project above opposite sides of an elongated transverse, horizontal,smooth, entry plate member 201. An tangle member 212 extendstransversely across the front of the machine and serves pivotally tomount each of the two web engaging members 2% and 202 by pivots 214 and215. The angle member 212 also serves, along with transverse member 213to support a pair of thin longitudinally running spaced support members203, 2% which support the entry plate 210. It should be noted that thepivots 214, 215, on opposite sides of the machine, are spaced apart adistance greater than the width of the material contemplated to be fedinto the machine. The members 200 and 202 are physically tied togetherby a transverse spacer member 216 which is pivotally mounted to thetrailing edges of members 2%, 202 at 218 and 220 so that the two members2%, 2G2 will move in tandem operation and will always present parallelsurfaces for contact with the edge of the sheet material 33 passingthrough the apparatus. The spacer member 216 is biased to the 'left asviewed in FIGS. 9 and 9b by means of a spring 226 which it attached atone end to member 212 by a pin 222 at the other end and to a pin 224- onmember 216. Thus, the web engaging members 2% and 292 will normallypresent curved edges 266 and 208 to the opposite edges of the sheetmaterial strip or panel 33, said edges always being parallel and selfadjusting and aligning so that the material 33 is always accuratelycentered as it is fed into the machine.

The measuring and control means 198 is mounted at the top of uprights194 and is spaced to the left of the alignment means 196 as viewed inFIGS. 1 and 9a. It will be noted that in FIG. 9a the upper portion ofmeans 198 comprises a pair of spaced, knurled-edge top wheels 22% and234?, best seen in FIGS. 9, 10 and 11, which wheels are adapted to restupon and engage the top surface of the web of material 33, as it isreceived from the alignment means 196. The knurled wheels are spacedlymounted and keyed upon a shaft 232 which is rotatably mounted at itsopposite ends in movable bearing blocks 234 and 235. The bearing blocks234, 235 are loaded by suitable spring mechanisms 236, 237 which areadjustable by a nut and bolt arrangement 238, 239 as shown in FIG. 10.The bearing blocks 234, 235 slide respectively between pairs of spacedapart track members 249, 241 and 242, 243 which are joined together attheir tops by spacer bars 244, 245. It will be noted that the spacerbars 244, 245 serve to mount the nut and bolt adjusting means 238, 239for loading the blocks 234, 235 as previously discussed, so that thewheels 228 and 230 may accommodate flaws in the material withoutbinding, as well as adjusting to Varying thicknesses of material.

As shown in FIGS. 90, 10 and 11, a pair of rotatable lower wheels 2.46and 247, which may be smooth surfaced is mounted on axially aligned butspaced shafts 248, 249 which in turn are mounted in bearing blocks 250,251 and 252, 263. This entire mechanism is fastened to transverse crossmember 254- which in turn is fastened to up rights 194. The wheels 246,247 are disposed in opposed relationship to top wheels 228 and 23! saidwheels 246 and 248 projecting a very slight distance above the majorplane of plate 201 through appropriate notches therein (see FIG. 9a). Itwill be observed that the arrangement is such that as the material 33 ispulled through the machine all four of the wheels will rotate, the topwheels 228 and 230 causing shaft 232 to rotate due to 2: the frictionalcontact of the knurled surfaces of the wheels with the material.

Shaft 232 is formed with an extension thereon which is located to theright as viewed in FIG. 9 so that as shaft 232 turns it causes a cam 255located at the end of the extension to rotate therewith. The cam 255 inturn is operable to actuate a switch 256 each time it makes one completerevolution. The function of switch 256 is to stop the moving clamp means199 (FIGS. 1 and 2) as immediately hereinafter in accurate relationshipto the linear movement of material 33 as it is fed into the machine. Theswitch 256 operates in the circuit shown in FIG. 4 which is discussed indetail hereinafter. The moving clamp mechanism 199 previously referredto forms a part of the feed means 36 for moving the material 33 throughthe machine. It extends from adjacent the measuring and control means198 to the out put side of the machine and comprises track means 257,258 spaced on opposite sides of the moving web. Disposed within thetrack means 257, 253 for cooperation therewith are a pair of spaceddriving members 259, 260, here shown in the form of endless toothed bandsaw blades which directly engage the material 33 to accomplish positivemovement of same through the machine. While it will be apparent that anyof a number of suitable toothed mechanisms may be used to engage theunderside of the web of the material to move it along, it has been foundparticularly expeditions to use band saw blade members because they areeasy to obtain, are available to rather accurate dimensions, and arerelatively inexpensive. The band saw blades 259, 26% are mounted formovement over idler wheels 251, 262 which in turn are mounted onuprights 193, and on driving wheel members 263, 264 which are mounted onuprights '94 at the outlet side of the machine and spaced from the idlerwheels. The idler wheels 261, 262 are located adjacent the relativelysmaller trailing end of entering plate 291 as shown in FIG. 9a. Thedriving members 263, 264 will be discussed in detail later and aredriven by suitable spaced upright drive shafts 265, 265 which, in turn,are driven by a constant speed DC. motor 267 (FIG. 3) which constantlyruns when the machine is in operation.

As shown diagrammatically in FIG. 3, a clutch brake mechanism 258 isdisposed intermediate the drive shafts 265, 266 and the motor 267. Theoutput side of the clutch-brake mechanism 253 is attached to a gear unit279 by a shaft 269. The output side of gear unit 279 comprises a pair ofoppositely disposed shafts 271, 27 1a which lead respectively to theupright drive shafts 265 and 266 which drive wheels 263, 264. Theclutch-brake 268 is preferably of the magnetic variety, as wellunderstood in the art and contains there within, a pair of electricallyenergized coils. The first of these coils 272 (FIG. 4) when energizedassures a positive driving connection and the second coil 274 whenenergized assures positive mechanical braking action so that no rotarymotion is transmitted to shaft 259. Thus, by alternatively electricallyenergizing the coils 272 and 274 in a manner to be later explained,positive action and inaction of the drive wheels and the driving toothedmembers 259, 260 is accomplished, and the speed and duration of feedingof the sheet or Web 33 may be in accurate timed relationship to themotion and sequence of the rest of the operating parts of the machine.

The material 33 is trapped between the smooth overhanging portions 292,293 of the track means 257, 258 and the teeth of the band saw members259, 260 (see FIGS. 14, and 16) for sliding movement along portions 292,293. The individual band saw members 259, 269 are mounted for engagementwith the web of material 33 at the edges thereof by a plurality ofrollers 27 6 which are spacedly and rotatably mounted on shafts 284. Theshafts 234 are mounted in sliding block members 278 which are slidablymounted in grooved track members 279. Mounted on the exterior of thetracks 257, 258 to prevent the band saw blades from slipping off rollers276 are spaced blocks 275 which are mounted at suitable intervals on thetracks 257, 258, the inner block being mounted on the track and theouter block being mounted on a bracket member 277 as shown in FIG. 15.The blocks 275 are preferredly made of a hard material such as tungstencarbide. The shafts 284 extend through relatively large holes 283 formedin the tracks and are mounted therein by springs 280 which are attachedto the ends of shafts 284 and to pins 282 mounted on members 292, 293.Each spring 280 causes the corresponding member 278, and hence roller276, and thereby members 259, 260 to be biased upwardly to a fixedposition so determined as to assure positive engagement with theunderside of the web of the material 33. Slide member 273 slidesupwardly within grooves 236 and 288 of member 279 until it engages a setscrew 289 which limits the upward extent of the movement of the slidemember 273 and hence of roller and band saw members 259, 26%. It will benoted that the band saw members 259, 26G are free to move downwardlyagainst the bias of springs 23%). The set screws 239 assure that theteeth of the band saw members 259, 260- .can be set to a correct heightfor positive material engagement without tending to bite tooaggressively or to saw through the plastic sheet material web 33. Thetracks 257 and 258 are adjustably mounted on the machine by slidingplates 297 (FIGS. 2 and 6) having elongated slots 297a therein. Theplates 297 are fastened to uprights 94 by suitable bolts so that thespace between the tracks 257, 258 may be adjusted. The idler wheels 261,262 are mounted on adjustment rods 295 as are drive wheels 263, 264 sothat the space therebet-ween may be adjusted as desired.

The driving Wheels 263, 264 (illustrated in FIGS. 12

I and 13) are mounted in suitable bearings 29% for rotation therein. Thebearings 293 are in turn mounted on width adjusting rods 295 (FIGS. 1and 2) and tension adjusting rods 296, the latter being attached toupright members 94. The wheel 263 is mounted on a keyed frustoconicalhub member 299 on shaft 265. The outer periphery of wheel 263 isprovided with a plurality of radially extending bores 30% having springloaded pins 301 mounted therein for engagement with complementaryindentations 302 on a shoe member 3&3 which embraces the periphery ofthe wheel 263-. (The construction of wheel 264 is identical, and wheel253 has been chosen for illustrative purposes.) The body portion ofannular member 363 tapers inwardly upwardly as shown in a manner tocause an annular peripheral liner member 364 of fibrous material such asbrake lining mounted on each wheel together with the band saw members259 to be biased in a downward direction. Thus, this configurationcauses the toothed band saw members 259, 260 mounted and moved thereonto be biased against the rollers 276. At the same time, the previouslydescribed spring loaded pins 3&1 provide a constant tension on the bandsaw members 259, 26d and also provide a friction clutch arrangement inthe event that the material 33 becomes jammed in the machine in the moldarea. It is important that a constant tension be kept on the members259, 269 to accomplish the accurate feeding of the precise amount ofmaterial as it is desired per cycle of the machine. The L-shaped incross-section member 303 and the brake band fiberous member 3134 areboth retained on the wheel 263 by a suitable annular retaining plate 305which may be bolted to the wheel 263 as shown in FIG. 12.

As mentioned hereinbefore, the DC. motor 267 is preferably running atall times and the feed mechanism driven thereby is intermittently drivenby the energizetion of coil 272 and de-energization of coil 274 ofclutch-brake 268. To this end, cam 3% is mounted on the end of lower camshafit 78 (FIG. 6) and when rotated (see Wiring diagram in FIG. 4)closes switch 388 to energize a relay 316 which in turn, de-energizesthe brake coil 274 and energizes clutch coil 272 to start the' drivewheels 263, 264 turning. It will be noted from FIG. 4 that a transformerinput 316 is shown with one side of the output 312 being connected to afull wave rectifier 314, the other side thereof being connected to relay315 through switches 256 and 3118 which are normally open and connectedin parallel. A normally open relay switch 318 is in series with themotion transmitting clutch energizing coil 272 of the clutch 26-8, and anormally closed relay switch 3-20 is connected in series with themechanically de-energizing coil 274 in the other relay circuit. Thus,closing either switch 256 or 308 by their respective cams will serve toenergize relay 316 to energize coil 272 and deenergize coil 274. Theactuating surfaces of cams 3% and 255 are so coordinated and timed thatfirst, cam 3G6 closes switch 303 whereby the drive wheels 263, 264 areturned to cause material 33 to be fed into the machine. This operationcauses top wheels 228, 230 of the measuring control means 193, and henceshaft 232 to rotate whereby cam 255 actuates switch 256. At this timethe cam 255 associated with measuring mechanism takes over control ofthe circuit from cam 3G6 and switch 3113, and cam 3116 causes switch 308to open. The circuit governing the movement of the feed mechanism thenremains under the control of the switch 256 which shuts Off the feedmechanism. In summary, the lower cam shaft 78 is operable to start thefeed mechanism in timed relation to the movement of the mold means 44and mandrel means 42, and the measuring and control means 199, by virtueof cam 255, is operable to stop the feed means at the precise instantwhen sufficient material 33, as measured by wheels 228, 230, has movedthrough the device to provide the predetermined amount of stocknecessary for one molding cycle.

A heater mechanism 322 is shown semi-diagrammatically and is disposedimmediately adjacent the mold and mandrel means of the machine. Theheater 322 may comprise, for example, a plurality of Nichrome, infra-redelements or other heaters as suitable and desired which are preferablymounted between a pair of spaced longitudinally extending rails 324 and326. The rails 324, 326 are each pivotally mounted at the machine endthereof as shown at 328 and 330. The other ends of rails 324, 326 areformed with pins 333, 334 (FIG. 1) which rest on spaced uprights 331,332 when the heater is in the position shown in FIG. 1. The uprights'331, 332 are attached to uprights 193 as shown. Second pins such as340, 342 are mounted on each side rail 324 and 326 a short distance frompins 333, 334 for attaching one end of the pair of spaced overheadcables 344 and 346, each of which is looped over a pulley 348 and has aweight 349, 350 attached to the other end thereof as shown. The weightsare preferred disposed within the channel-shaped uprights 94, andprovide, along with the position of the pulley, a counter balance with amechanical advantage such that they are sufiicient to maintain theheater in a balanced upright position when it is so positioned, and yetare insuflicient to cause the heater to move of its own accord to thisupright or spaced position from the horizontal position shown in FIG. 1of the drawings. Thus, when a jam-up occurs in the machine such that theweb of material 33 is stopped beneath the heater 322, the heater 322 ismanually pivotally moved to its spaced or upright position to preventthe material 33 from melting and dropping down to coat under portions ofthe machine and/or to avert the possibility of the web starting a fire.

Operation Assuming the parts are in the position shown in FIG. 17, andafter an initial warm-up period, a cycle of the apparatus can bediscussed as follows: The motor 52 is energized by suitable means (notshown) which in turn causes operation and rotation of the upper andlower cam shafts 86 and 78. The upper cam shaft 86 in turn causesmovement of the cams 175, 176 which in turn control the movement of themandrel means 42. The rotation of the lower cam shaft 78 causesrotational movements of cams 143, 144 (and accompanying cam flanges 145,146) cam 98 and cam 3116. Cam 3596 is located on the end of the shaftand controls the switch 308 for the intermittent starting of the feedmechanism. The web of sheet material 33 is fed in predetermined measuredincrements from the supply roll 34 across plate 29-1 through thealignment means 196 and the measuring and control means 198 by thespaced band saw members 259, 263 which move the selected amount of theweb of material beneath the heater 324 and subsequently into the areabetween the mold and mandrel means. The relative position of the partsduring the cycling of the device is shown in FIGS. 17-25, the startingposition being as shown in FIG. 17. At this time the mold cavity 132 isin its lowermost position with the knock-out plug 156 in its uppermostposition and the upper clamp means 182 remaining substantially in thesame position throughout the cycle. The top and bottom cam shafts 86-78rotate to cause the relative movements of the parts. (It should be notedat this juncture that the semi-diagrammatic views 17 through 24 showboth of the cam shafts 8678 operating in a clockwise direction; in pointof fact, when the machine is operating, one of the cam shafits isoperating in a clockwise direction and the other is operating in acounter-clockwise direction as shown in FIG. 5.) As the cam shaftsrotate approximately to the position shown in FIG. 18, it will be notedthat the upper clamp means 182 and lower clamp means 96 now firmlyengage the web 33 of material, the lower clamp means 96 having beenmoved almost immediately from its spaced position to the web engagingposition shown in FIG. 18 by cam 126. The quick clamping of the materialearly in the cycle by the clamp means 96182 is important to high speedoperation. The mold cavity 132 has started its upward movement towardsits uppermost extended position and the mandrel166 has moved downwardlyto a position of contact with the web 33 of plastic material. Chillingof the web in the portions contacted by the clamp means 96, 182accurately determines the area of material to be drawn by each mandrel.As the upper and lower cam shafts 36, 78 continue to rotate, each uppermandrel member 166 moves to the position shown in HG. 19, being extendedto its greatest extent and thereby completing the substantial portion ofthe mechanical draw of the material 33 relative to the clampingengagement of the upper and lower clamping means 182, 96. The mold 132continues to move upwardly causing slightly more mechanical drawing ofthe material 33, the mold continuing upwardly until it reaches theposition shown in FIG. 20 at which point the annulus 188 surrounding themandrel and the mold serve to trap and clamp the material between moldlip 160' by the shoulder 162 and the leading edge 190 of annulus 133 asshown in enlarged detailed section in FIG. 21.

Air under pressure (shown diagrammatically by arrows in FIG. 22) is thenadmitted from the mandrel side of the Web forcing the web 33 of materialto leave engagement with such features of the mandrel 166 as it contactsand to move into contact with the cooled walls of the mold cavity 131.The mold cavity cools the material 33 and causes it to set almostinstantaneously. The cam shafts 86, 78 then continue to rotate, and asshown in FIGS. 23 and 25, the top cam causes the mandrel annulus 183 tomove down slightly so that the leading edge of the annulus 1'88 shearsthe material against the shoulder 162 surrounding the mold lip 160. Thiscauses the formed container 32 to be severed from the remaining portionsof the web which are now scrap material. The parts then return to theposition shown in FIG. 24 (which is identical with the position shown l3in FIG. 17) so that container 32 sits on the knockout plug 156whereafter the election means 58, in the form of an air pressure nozzle,blows the finished container towards a suitable chute (not shown) for acontrolled gathering of the formed items for subsequent packagingthereof.

The construction of the machine 3% is such that tl". entire cyclerequires a matter of only a few seconds, for such a high speedoperation, extremely fast responding and accurate feed means isprovided. lt will be noted that the feeding mechanism must not onlyrespond very rapidly and accurately, but must be exceedingly rugged sothat it can feed the required amount or" material in the short timeinterval permitted in fast cyclin 'lhe next increment of material mustbe moved into position while the machine is between the position shownin FIG. 23 and a position intermediate the positions shown in FIGS. 17and 18.

It is important to note that as the machine is started up after aprolonged shut down, it is not unusual to have at first a large lam-upof material in the vicinity of molds and mandrels. This occurs becausethe machine is designed to be operative at such a high production speedthat it appears to take a few minutes to get all parts coordinated torun the machine smoothly. ft hen this jam-up of material occurs, it isnot unusual to get live, six or seven thicknesses of material in thevicinity of the mold and mandrel. In machines not having the deflectingshaft mechanisms such as 73, 86 shown and described hereinbefore,something would have to give way, the most likely parts being the moldsor the mandrels which are very expensive. However, in the instantmachinery, due to the resilience and/ or deilection of the shafts 78,'36 and due to the bearing structure and all of the associated echanism,the jam-ups are accommodated and none of the machine parts are subjectedto breakage. Also, in the instant machine, the deflection of the shafts78, 85 and the design described allows an effect similar to a type of aresilient back pressure to provide a smooth type of operation whicheliminates much of t e pounding associated with most ram-types ofmolding machines known heretofore.

Although a specific embodiment has been shown and described, it is withfull awadeness that many modifications thereof are possible. Theinvention, therefore, is not to be restricted except insofar as isnecessitated by the prior art and by the spirit of the appended claims.

What is claimed as the invention is:

l. A machine for producing thin wall plastic items from a web of plasticmaterial comprising, a movable mold means and a movable mandrel meansadapted to engage a portion of an elongated Web of plastic material fromopposite sides thereof to form items of predeteri ined shape, firstactuating means comprising a first rotatably driven shaft having firstcam means thereon rotating in a first direction operable to move saidmold means relative to said web of material, second actuating meansspaced from said first actuating means and comprising a second rotatablydriven shaft having second cam means thereon rotating in a seconddirection and operable to move said mandrel means relative to said web,motor means operable to drive said spaced first and second actuatingmeans, and means associated with each of said first and second actuatingmeans comprising spaced spheroidal bearing means for said first andsecond rotatable shafts, said spaced bearing means accommodating a widerange of de tections of said shafts to afford resilient mounting thereofto accommodate a jam-up of web material between said mold and mandrelmeans without deleteriously affecting said first and second actuatingmeans, said mold means or said mandrel means.

2. The machine set forth in claim 1 wherein connection means is providedintermediate the motor means and the rotating shafts, said connectionmeans comprising a driving member engaging at least one of said shaftsid to impart rotational movement thereto while accommodating a largerange of non-rotational movement of said shaft.

3. A machine for producing thin wall plastic items from a web of plasticmaterial comprising, movable mold means and movable mandrel meansadapted to engage said Web of material from opposite sides thereof toform items of predetermined shape, supply means of plastic materialspaced from said mold and mandrel means, temperature control means forsaid plastic material disposed in temperature controlling relationshipwith said plastic material intermediate said supply means and said moldand mandrel means, first actuating means operable to move said moldmeans relative to said web of material, second actuating means spacedfrom said first actuating means and operable to move said mandrel meansrelative to said Web of material, motor means operable to drive saidspaced first and second actuating means, feed means adapted to move saidWeb of material from said supply means to said mold and mandrel meansand therebeyond, drive means operative to drive said feed means, controlmeans associated with said feed means and one of said actuating meansfor operating said drive means selectively to cause said feed means tomove the plastic web through said machine in timed relation to movementof said mold and mandrel means, and means as sociated with each of saidfirst and second actuating means affording resilient mounting thereof toaccommodate a jam-up of web material between said mold and mandrel meanswithout deleteriously affecting said first and second actuating means,said mold means or said mandrel means.

4. A machine for producing thin wall plastic items from a web of plasticmaterial comprising movable mold means and movable mandrel means adaptedto engage said Web of material from opposite sides thereof to form itemsof predetermined shape, supply means of plastic material spaced fromsaid mold and mandrel means, temperature control means for said plasticmaterial disposed in temperature controlling relationship With saidplastic material intermediate said supply means and said mold andmandrel means, first actuating means operable to move said mold meansrelative to said web of material, second actuating means spaced fromsaid first actuating means and operable to move said mandrel meansrelative to said web of material, first motor means operable to drivesaid spaced first and second actuating means, feed means adapted to movesaid Web of material from said supply means to said mold and mandrelmeans and therebeyond, drive means comprising continuously operatingsecond motor means and clutch means operative to drive said feed means,and control means associated with said feed means and one of saidactuating means for energizing said clutch means to cause said secondmotor means to drive said feed means to intermittently move the plasticWeb through said machine is timed relation to movement of said mold andmandrel means.

5. A machine for producing plastic items from a web of plastic materialcomprising, movable mold means and movable mandrel means adapted toengage said Web of material from opposite sides thereof to form items ofpredetermined shape, supply means of such plastic material spaced fromsaid mold and mandrel means, first and second actuating means operablerespectively to move said mold and mandrel means relative to said Web ofmaterial, motor means operable to drive said first and second actuatingmeans, feed means adapted when driven to move said web of material fromsaid supply means to said mold and mandrel means and therebeyond, drivemeans operative when energized to drive said feed means, and on-oflcontrol means associated with said feed means and one of said actuatingmeans for energizing and deenergizing said drive means, actuation ofsaid on-olf control means by one of said actuating means causing saiddrive means to drive said feed means to move the plastic 15 Web throughsaid machine in timed relation to movement of said mold and mandrelmeans.

6. A machine for producing plastic items from an elongated thin web ofplastic material comprising, movable mold means and movable mandrelmeans adapted to engage said web of material to form items ofpredetermined shape, supply means of such plastic material spaced fromsaid mold and mandrel means, temperature control means for said plasticmaterial disposed in temperature controlling relationship with saidplastic material intermediate said supply means and said mold andmandrel means, first and second actuating means operable to move saidmold and mandrel means relative to said web of material, motor meansoperable to drive said first and second actuating means, feed meanscomprising alignment means, measuring and control means and web engagingdrive means adapted to align, measure and move said web of material fromsaid supply means to said mold and mandrel means and therebeyond, drivemeans for said feed means including second motor means and clutch-brakemeans operable when energized in one manner to drive said web engagingdrive means, shut off control means associated with said measuring meansof said feed means and said clutch-brake means for energizing the latterin another manner and stopping said web engaging drive means andenergizing control means associated with one of said actuating means andsaid clutch-brake means to energize the latter in said one manner andthereby to cause said web engaging drive means of said feed means tomove said web of material from said supply means past said temperaturecontrol means to a position adjacent said mold and mandrel means andtherebeyond in increments determined by said measuring means.

7. An apparatus for use with a web of plastic material comprising motormeans adapted to drive first and second vertically spaced cam shafts,first and second cam means mounted on said first cam shaft, third cammeans mounted on said second cam shaft, movable mold means actuated bysaid first cam means and adapted to engage said plastic material,movable mandrel means actuated by said third cam means and cooperablewith said mold means for engaging and deforming said Web of material,and clamp means comprising a first movable clamp member actuated by saidsecond team means and a relatively fixed clamp member whereby saidmovable clamp member is actuated independently of said mold member intimed relation thereto.

8. A machine for producing thin wall plastic items from a web of plasticmaterial comprising, movable mold means and movable mandrel meansadapted to engage said Web of material from opposite sides thereof toform items of predetermined shape, first and second spaced relativelymovable clamping means operable clampingly to engage said web ofmaterial prior to engagement thereof by said mold and mandrel means,first actuating means operable to move said mold means relative to saidweb of material, means associated with said first actuating means andindependent of said mold means for actuating one of said clamping meansrelative to the other, second actuating means spaced from said firstactu atin-g means and operable to move said mandrel means relative tosaid web of material, and means operable to drive said spaced first andsecond actuating means.

9. A machine for producing plastic items from a web of plastic materialcomprising, movable mold means and movable mandrel means adapted toengage said web of material to form items of predetermined shape, supplymeans of plastic material spaced from said mold and mandrel means, andfeed means for said machine comprising alignment means, measuring andcontrol means for measuring the amount of material passing therethrough,and web driving means adapted to move said web of material from saidsupply means to said mold and mandrel means and therebeyond, said webdriving means including a pair of spaced pulley members at least one ofwhich is driven and a circumferentially continuous member mounted onsaid spaced members, said circumferentially continuous member having atoothed surface adapted positively to engage said plastic material tocontrol the movement thereof, and means on said measuring and controlmeans for controlling the movement of said driven pulley in accordancewith measured amounts of material passing therethrough.

10. A machine comprising, a base and a crown vertically fixed above saidbase, a first cam shaft mounted on said base, a second cam shaft mountedon said crown, an upper cradle member dependingly mounted forreciprocatory movement in accordance with rotational movement of saidsecond cam shaft, a lower cradle member mounted above said first camshaft for reciprocatory movement in accordance with rotational movementof said first cam shaft, mandrel means mounted for movement by saidupper cradle member, mold means mounted for movement by said lowercradle member, and quick easily removable force transmitting adjustmentmeans interposed respectively between said upper cradle member and saidmandrel means and said lower cradle member and said mold means wherebythe relative spaced relationship between said mold and mandrel means maybe changed without dismantling said machine.

11. An apparatus for use with a web of plastic material comprising,vertically spaced first and second cam shafts, motor means adapted todrive said first and second cam shafts, first and second cam meansmounted on said first cam shaft, third cam means mounted on said secondcam shaft, movable mold means actuated by said first cam means andadapted to engage said plastic material, movable mandrel means actuatedby said third cam means and coopera'ole with said mold means forengaging and deforming said web of material, and clamp means comprisinga first movable clamp member actuated by said second cam means and arelatively fixed clamp member, said second cam means comprising acentrally located cam and a pair of spaced plates supporting a roller todefine a carriage means, said roller engaging said cam and said spacedplates being connected to said lower cam means, whereby said movableclamp member is actuated independently of said mold member in timedrelation thereto.

References Cited in the file of this patent UNITED STATES PATENTS266,100 Collinge et al. Oct. 17, 1882 516,376 Kulage Mar. 13, 1894951,579 Rigby Mar. 8, 1910 1,181,964 Bohlman May 2, 1916 1,189,263Krauth July 4, 1916 1,253,316 Welland Jan. 15, 1918 1,598,911 Hochmuthet a1 Sept. 7, 1926 1,904,268 Bronson Apr. 18, 1933 2,282,423 KopitkeMay 12, 1942 7 2,298,492 Longfield Oct. 13, 1942 2,565,162 Wixon et a1Aug. 21, 1951 2,580,883 Borkland Jan. 1, 1952 2,844,858 Assmann July 29,1953 2,836,852 Butzko June 3, 1958 2,962,758 Politis Dec. 6, 19602,967,328 Shelby et al. Jan. 10, 1961

1. A MACHINE FOR PRODUCING THIN WALL PLASTIC ITEMS FROM A WEB OF PLASTICMATERIAL COMPRISING, A MOVABLE MOLD MEANS AND A MOVABLE MANDREL MEANSADAPTED TO ENGAGE A PORTION OF AN ELONGATED WEB OF PLASTIC MATERIAL FROMOPPOSITE SIDES THEREOF TO FORM ITEMS OF PREDETERMINED SHAPE, FIRSTACTUATING MEANS COMPRISING A FIRST ROTATABLY DRIVEN SHAFT HAVING FIRSTCAM MEANS THEREON ROTATING IN A FIRST DIRECTION OPERABLE TO MOVE SAIDMOLD MEANS RELATIVE TO SAID WEB OF MATERIAL, SECOND ACTUATING MEANSSPACED FROM SAID FIRST ACTUATING MEANS AND COMPRISING A SECOND ROTATABLYDRIVEN SHAFT HAVING SECOND CAM MEANS THEREON ROTATING IN A SECONDDIRECTION AND OPERABLE TO MOVE SAID MANDREL MEANS RELATIVE TO SAID WEB,MOTOR MEANS OPERABLE TO DRIVE SAID SPACED FIRST AND SECOND ACTUATINGMEANS, AND MEANS ASSOCIATED WITH EACH OF SAID FIRST AND SECOND ACTUATINGMEANS COMPRISING SPACED SPHEROIDAL BEARING MEANS FOR SAID FIRST ANDSECOND ROTATABLE SHAFTS, SAID SPACED BEARING MEANS ACCOMMODATING A WIDERANGE OF DEFLECTIONS OF SAID SHAFTS TO AFFORD RESILIENT MOUNTING THEREOFTO ACCOMMODATE A JAM-UP OF WEB MATERIAL BETWEEN SAID MOLD AND MANDRELMEANS WITHOUT DELETERIOUSLY AFFECTING SAID FIRST AND SECOND ACTUATINGMEANS, SAID MOLD MEANS OR SAID MANDREL MEANS.